CN104533608B - Double-piston rotor internal-combustion engine - Google Patents
Double-piston rotor internal-combustion engine Download PDFInfo
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- CN104533608B CN104533608B CN201410813152.3A CN201410813152A CN104533608B CN 104533608 B CN104533608 B CN 104533608B CN 201410813152 A CN201410813152 A CN 201410813152A CN 104533608 B CN104533608 B CN 104533608B
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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Abstract
The invention discloses a kind of double-piston rotor internal-combustion engine, its first rotor includes that rotating shaft dish, one end of rotating shaft dish are two first piston bodies, and the other end is the first gyroaxis equipped with the first oval gear；The bottom surface of cover plate is connected with the end face of first piston body；The second gyroaxis that second rotor includes, its one end is provided with two the second piston bodies, and the other end is equipped with the second oval gear；Second gyroaxis is threaded onto in the axis hole of the first gyroaxis, and is threaded onto together in the axis hole of dish；The upper and lower end plate of dish ring flange with burning chamber shell and gear-box respectively is connected with；Bottom gear-box, axis hole is provided with power output gear axle；The upper oval gear of two double oval gear axles engages with the first oval gear and the second oval gear respectively, lower oval gear engages with two oval gears on power output gear axle respectively.Oil consumption of the present invention is low, power to weight ratio is high, output moment of torsion is big, it is light, simple and compact for structure to vibrate；Easily design, anufacturability are good.
Description
Technical field
The present invention relates to technical field of internal combustion engines, particularly to rotary-piston class double-piston rotor internal-combustion engine.
Background technology
Heat engine is to convert heat energy into the device of mechanical energy, and internal combustion engine is an important kind of heat engine, and internal combustion engine is main
Including ignition system, combustion system, drive system, cooling system, oil supply system, lubricating system etc..
Since about 1898 Christian era crankshaft connecting rod type internal combustion engine invent so far, in surface car, shipping and various dynamic
In power equipment, crankshaft connecting rod type internal combustion engine obtains most commonly used application, and has greatly accelerated the historical progress of the mankind.Bent axle
The basic functional principle of connecting rod type internal-combustion engine, is that the gases at high pressure promotion that piston is burnt in cylinder moves up and down, and leads to
Cross connecting rod band dynamic crankshaft to rotate, by the gearing of crankshaft-and-connecting-rod, the straight reciprocating motion of piston is converted into bent axle
Unidirectional rotary motion, thus realize heat to power output and the power output of crankshaft connecting rod type internal combustion engine.
The key technical indexes of evaluation internal combustion engine has power to weight ratio, and (power/weight ratio is sometimes also adopted by cylinder power per liter and refers to
Mark), oil consumption rate, anufacturability, working service life-span etc..For crankshaft connecting rod type internal combustion engine, engine power output is logical
Cross what the crankshaft connecting rod type drive system of piston, connecting rod and bent axle triplicity completed.This internal combustion engine mainly has as follows
Structural disadvantage:
1, in crankshaft connecting rod type passes cylinder of internal-combustion engine, gaseous mixture is short for burning time pressure maximum, volume minimum when,
Piston is the most descending, makes incomplete combustion, and exhaust gas concentration is high, and work doing efficiency is low.Existing crankshaft connecting rod type internal combustion engine is in order to carry
High engine performance, all arrives before upper dead canter advanced ignition in various degree or oil spout at piston in order to allow gaseous mixture
Combustion chamber volume minimum when, burning is faster, more completely, it is thus possible to obtain bigger power output, and reduces electromotor
Discharge exhaust gas concentration, but do so also creates certain negative interaction: and because of advanced ignition, in-cylinder pressure drastically raises, and blocks
Piston stroking upward, adds compression negative work, and easily causes combustion knock phenomenon.This contradiction is at existing crankshaft connecting rod type internal combustion
Machine exists all the time.
2, during crankshaft connecting rod type internal combustion engine operation, the connecting rod force direction periodically-varied to piston, and
When engine power output is maximum, the active force of piston is also reached near maximum by connecting rod along cylinder wall surface normal direction, by
This causes the frictional power loss between piston and cylinder very big, and is easily caused between piston and cylinder surface and causes because of friction
Damage.
3, in the operation process of crankshaft connecting rod type internal combustion engine, piston is in a kind of reciprocating motion state all the time, during air inlet
Piston the most quickly enters compression travel in lower dead center moment, thus does not has more time inspiration more when cylinder body volume maximum
Fresh mixing oil gas, during aerofluxus, piston the most quickly enters suction stroke to top dead centre moment, so that volume of cylinder is minimum
Time do not have the more time to allow waste gas farthest discharge, these situations the most all affect more fresh mixing oil gas and enter
Enter cylinder, thus cause engine breathing efficiency low, make the raising of HP, hp/litre be affected by certain.
4, crankshaft connecting rod system is not axial symmetry parts, the vibration caused by crankshaft connecting rod system during internal combustion engine operation
Greatly, noise is big；Crankshaft connecting rod system has much difficulty in healing weighing apparatus, and its manufacturing process is more complicated, and cost is high；In use, piston, bent axle are even
Linkages etc. are easy to wear, and maintenance cost is high；The internal combustion engine limit speed using crankshaft-link rod is low, seriously constrains electromotor merit weight
The raising of ratio.
5, the structure such as the air throttle of crankshaft connecting rod type internal combustion engine, crankshaft-link rod is complicated, takes up room big, causes electromotor to be tied
Structure is the compactest.
Since entering for 20th century, manifesting of energy crisis, and problem of environmental pollution is intensification, promotes to bent axle even
The design improvement of rod-type internal combustion engine.At present, the design through multiple stages such as pressurized combustion, EFI improvement improves, bent
The technical performance index of axle connecting rod type internal-combustion engine has reached ultimate attainment, but is tied by above-mentioned crankshaft connecting rod type internal combustion engine
The restriction of structure shortcoming, wants to obtain the internal combustion engine of more preferable technical performance index, only uses new IC Engine Design scheme.
As far back as 20 beginnings of the century, occur in that a kind of internal combustion engine being referred to as triangle rotor type electromotor, and obtain later
Relatively broad application.Compared with crankshaft connecting rod type internal combustion engine, triangle rotor type electromotor uses the power of gear-driven form
Output mechanism, drive mechanism axial symmetry is preferable, and Engine Limit rotating speed is high, and therefore power to weight ratio is outstanding, and structure is the most more
Compact.But in place of triangle rotor type electromotor there is also some shortcomings.Such as gas in-cylinder combustion is insufficient, oil consumption is excessive, defeated
Shaft moment of torsion is too small, cylinder seal difficulty etc..This is because combustion gas acts on rotor side surface in rotary polygonal piston engine cylinder
The bulbs of pressure are divided into two power, try hard to recommend dynamic output shaft for one and rotate, and another power points to output shaft center, thus cause whole
The output moment of torsion of machine is too small；Make combustion rate too low because its cylinder is long and narrow, excessive oil consumption；Because using the gas of special shape
Cylinder, result in cylinder processing and manufacturing and difficulty that cylinder seal manufactures and designs.If above-mentioned triangle rotor type electromotor exists
Dry problem, causes it to be difficult to promote the use of on a large scale in today that energy crisis and problem of environmental pollution are the most serious.
Enter 21 century, on the one hand, from the angle of social need:
1, energy crisis is more significantly, and environmental problem is on the rise, and the discharge standard of internal combustion engine improves constantly, thus promotes
The mankind find the internal-combustion engine technology of more energy-conserving and environment-protective.
2, in the family-sized car field that car and boat power set field, especially market are huge, by battery durable and safety,
The restriction of charging public utility construction coverage etc., the family-sized car market share of the purest motorized motions
Rate is the lowest, and the internal combustion engine of oil electricity mixed form is by real for the green power device becoming the family-sized car etc. of future city society
With selection.
3, at military technological field, the battlefield surroundings of Future Information, will further facilitate various unmanned vehicle equipment
Innovation Input, other power set such as relative aero-turbine, internal combustion engine is with its obvious low oil consumption, the long-life, low
The technical advantages such as cost, will continue to occupy one seat in unmanned vehicle power set field.
4, other aspects, as in emerging General Aviation market segment and model plane industries etc. such as personal aircrafts, internal combustion engine will
Continue its important power set role and status.
On the other hand, from the angle of internal-combustion engine technology development:
1, crankshaft connecting rod type internal combustion engine improves through some designs, and its technical performance has reached substantially to the limit, its technology
Performance indications power to weight ratio, oil consumption rate, anufacturability, working service life-span etc. are difficult to reach higher requirement.
2, triangle rotor type electromotor is a breakthrough of internal-combustion engine technology, but its high oil consumption, low output moment of torsion, seal tired
The technology weaknesses such as difficulty make it be difficult to become the main body of a new generation's internal-combustion engine technology.
Although 3, triangle rotor type electromotor has many technology weaknesses, but its brand new form of using, open
New design philosophy, opens the beginning of " rotary-piston class internal combustion engine ", is expected to solve many structures of crankshaft connecting rod type internal combustion engine
Property shortcoming, so in today of 21 century, occur in that the patent of invention of more " rotary-piston class internal combustion engine " class.But the most at present
Till, in such patent of invention, some patents are the mutation of crankshaft connecting rod type internal combustion engine, and its structure still retains crankshaft-link rod
The parts of shape, the performance that have impact on internal combustion engine realizes；The design of some patent structures is excessively complicated, have impact on the merit weight of internal combustion engine
Ratio, anufacturability, working service life-span etc.；Some patents lack Quantitative design and the analysis of necessity, according to its conceptual design
Manufacture product and do not actually reach the technical performance of patent nominal.
In sum: 21 century needs the technology such as a kind of power to weight ratio, oil consumption rate, anufacturability, working service life-span to refer to
Indicate the internal-combustion engine technology of important breakthrough, and " rotary-piston class internal combustion engine " is likely to become and meets these technical requirements
A new generation's internal-combustion engine technology.
Summary of the invention
It is an object of the invention to provide double-piston rotor internal-combustion engine, the excellent design reason of " rotary-piston " has been used for reference in this invention
Read, by fundamental difference in crankshaft connecting rod type internal combustion engine, be also substantially distinguished from the heating power transformational structure of triangle rotor type electromotor
Design, it is achieved internal combustion engine is dashed forward the great of the key technical indexes such as power to weight ratio, oil consumption rate, anufacturability, working service life-span
Broken, to meet mankind's use demand to internal-combustion engine technology.
The present invention takes techniques below scheme to realize above-mentioned purpose.
First technical scheme of the present invention: double-piston rotor internal-combustion engine, it is characterised in that: the first rotor is Y-shaped structure, bag
Including rotating shaft dish, one end of rotating shaft dish is two first piston bodies with the first gyroaxis axisymmetrical, and the other end is provided with first
Gyroaxis, the termination of the first gyroaxis is provided with keyway, and the first gyroaxis axle center is provided with axis hole；
Cover plate is garden plate-like, and the centre of cover plate is provided with the boss of band central through hole, and the periphery of cover plate is provided with chimb；Lid
The bottom surface of plate is connected with first piston body end face；
Second rotor is T-shaped structure, and is provided with the second gyroaxis, and one end of the second gyroaxis is provided with and axisymmetrical
Two the second piston bodies, the other end of the second gyroaxis offers keyway, and the periphery of first piston body and the second piston body is straight
Footpath is equal；
The Pan Zhou center of dish is provided with axis hole, and the two ends of dish axle connect upper end plate and lower end plate, and upper end plate is grid
Shape, upper end plate periphery and lower end plate periphery are provided with screw；Second gyroaxis is threaded onto in the axis hole of the first gyroaxis, and first
Gyroaxis and the second gyroaxis are all threaded onto in the axis hole at Pan Zhou center, are set with burning outside first piston body and the second piston body
Room housing；
Burning chamber shell is in peviform, and the periphery at the bottom of room is provided with ring flange, and ring flange is provided with screw, burning chamber shell
Periphery is provided with porting, and the offside of burning chamber shell porting is provided with the pilot hole of spark plug/fuel injector, and spark plug/
Fuel injector is fixedly installed in pilot hole；The upper end plate of dish is adjacent with the rotating shaft dish of the first rotor, the upper end plate of dish
Screw is bolted with the screw of burning chamber shell ring flange；
Gear-box is peviform, and bottom it, centre is provided with axis hole, and the periphery of gear-box upper end case mouth is provided with ring flange, method
Blue dish is provided with screw and the valve snail hole, lower end with dish is bolted；The axis hole axis both sides of gear-box are provided with double ovum
Shape gear shaft, double oval gear axles are equipped with upper oval gear and lower oval gear；Second gyroaxis and the first gyroaxis are threaded onto
Dish axis hole, and axle head is positioned at gear-box, the axle head of the first gyroaxis is equipped with the first oval gear, the axle of the second gyroaxis
Hold equipped with the second oval gear, the first oval gear and the second oval gear respectively with double oval gear axles of both sides in gear-box
Upper oval gear engagement, bottom gear-box, axis hole is provided with power output gear axle, and power output gear axle is provided with up and down
Two staggered side by side oval gears, and engage with the lower oval gear of double oval gear axles of both sides in gear-box respectively.
Described dish can be monolayer card, is provided with axis hole in the middle of card, and card periphery offers screw.
In the present invention, burning chamber shell, the first rotor, cover plate, the second rotor are jointly separated out four and are isolated from each other and volume
Variable cylinder, during internal combustion engine operation, the uniform rotation campaign on power output gear axle respectively through two-way, every road
Include into the transmission conversion of two oval gear groups of series relationship, be converted into the first rotor and the bitrochanteric have fixing
The periodicity variable speed motion of phase contrast, the first rotor and bitrochanteric rotating speed and relative angular position cyclically-varying, should
Four cylinder the most periodically increase and decrease volumes, and be the most periodically in air-breathing, compress, do work, exhaust stroke,
Thus cylinder of internal-combustion engine produces circulation merit, and outwards export power by power output gear axle.
Second technical scheme of the present invention: double-piston rotor internal-combustion engine, it is characterised in that: burning chamber shell a in peviform,
Basin mouth periphery is provided with ring flange, is provided with the first rotor a and the second rotor a in burning chamber shell a；The first rotor a is Y shape
Part, its one end is two first piston body a of the first gyroaxis a axisymmetrical, and the other end is provided with keyway, the first rotor a's
First gyroaxis a axle center is provided with manhole；Second rotor a is T-piece, and its one end is the two of the second gyroaxis a axisymmetrical
Individual second piston body a, the other end is provided with keyway；Second gyroaxis a is set in the manhole of the first rotor a；
Dish a includes upper disk surface and lower card, and the center of described upper disk surface and lower card is provided with through hole and passes through
Axle sleeve connects, and the upper and lower card of dish a the most all offers screw, and the keyway end of the first rotor a and the second rotor a is worn
Being loaded in the axle sleeve of dish a, the upper disk surface of dish a is adjacent with the first rotor a, and the upper disk surface screw of dish a passes through spiral shell
Bolt is fixing with burning chamber shell a flange plate screw hole to be connected；The lower card screw of dish a is by bolt and gear-box a ring flange
Screw is fixing to be connected；
Gear-box a is peviform, and bottom it, centre is provided with axis hole, and the periphery of gear-box a upper end case mouth is provided with ring flange,
Ring flange is provided with screw and is connected with the lower card screw of dish a by bolt；Axis hole in the middle of bottom gear-box a is provided with
Power output gear axle a, first, second gear shaft is symmetrically arranged on the axis both sides of power output gear axle a, the first gear shaft
Upper end roller gear is installed, the upper end of the second gear shaft is provided with roller gear, the lower end of the first gear shaft is provided with ovum
Shape gear, the lower end of the second gear shaft are provided with oval gear, and two oval gear axles are separately installed with oval gear, power
Being provided with oval gear on output gear shaft a, the keyway end of the first gyroaxis a and the second gyroaxis a is separately installed with Cylinder Gear
Wheel and corresponding engage respectively with the roller gear of the upper end of first, second gear shaft, the lower end of first, second gear shaft avette
Gear engages with the oval gear on two oval gear axles respectively, and oval gear on two oval gear axles is simultaneously and power
Oval gear engagement on output gear shaft a.
Described dish a can be monolayer card, is provided with axis hole in the middle of card, and card periphery offers screw.
In the present invention, burning chamber shell a, the first rotor a, the second rotor a, dish a are jointly separated out four and are isolated from each other
And the cylinder of variable volume, during internal combustion engine operation, the uniform rotation campaign on power output gear axle a is respectively through two
Road, every road includes into the transmission conversion of two oval gear groups of series relationship, is converted into the first rotor a and the second rotor a
Have fixed skew periodicity variable speed motion, the first rotor a and the rotating speed of the second rotor a and relative angular position week
Phase property changes, these four cylinder the most periodically increase and decrease volumes, and is the most periodically in air-breathing, compresses, does
Merit, exhaust stroke, thus cylinder of internal-combustion engine produces circulation merit, and outwards export power by power output gear axle a.
Two technical schemes of summary, observe from power output gear shaft to the drive connection of rotor, power output gear
Uniform rotation campaign on wheel shaft is respectively through two-way, and the transmission of two oval gear groups that every road includes into series relationship turns
Change, be converted into the first rotor and the bitrochanteric periodicity variable speed motion with fixed skew.So that by including
The volume periodically increasing successively of four cylinders that the first rotor and the second rotor are separated out jointly at interior multiple engine components
Subtract change, and be the most periodically in air-breathing, compress, do work, exhaust stroke, thus realize the heat to power output of internal combustion engine and dynamic
Power exports.
Double-piston rotor internal-combustion engine provided by the present invention, has following beneficial effect: can significantly reduce and start
Engine oil consumption, improves fuel economy, improves engine exhaust emission；The power to weight ratio of electromotor can be greatly improved；Structure letter
Single, anufacturability is good；Vibration and noise level are low, and smooth running, moving component is few, and the working service life-span is long；Compact conformation,
Power output moment of torsion is big；Electromotor multiple design parameter adjustable；Only needing the least structure design to adjust, the present invention can change
For high performance pump.
Accompanying drawing explanation
Fig. 1 is the perspective view of the present invention the first technical scheme.
Fig. 2 is the perspective view of the first rotor in the present invention the first technical scheme.
Fig. 3 is the perspective view of the present invention the first technical scheme cover plate.
Fig. 4 is the first rotor and the perspective view of cover plate combination in the present invention the first technical scheme.
Fig. 5 is bitrochanteric perspective view in the present invention the first technical scheme.
Fig. 6 is the perspective view of dish in the present invention the first technical scheme.
Fig. 7 is the front view of burning chamber shell in the present invention the first technical scheme.
Fig. 8 be in Fig. 7 A-A to sectional structure schematic diagram.
Fig. 9 is the perspective view of burning chamber shell in the present invention the first technical scheme.
Figure 10 is the perspective view of oval gear in the present invention the first technical scheme.
Figure 11 is the perspective view of double oval gear axles in the present invention the first technical scheme.
Figure 12 is A direction view in Figure 11.
Figure 13 is the perspective view of the present invention the first technical scheme medium power output gear shaft.
Figure 14 is the perspective view of the present invention the first technical scheme middle gear tank shell.
Figure 15 is the perspective view of the present invention the second technical scheme.
Figure 16 is the perspective view of the first rotor a in the present invention the second technical scheme.
Figure 17 is the perspective view of the second rotor a in the present invention the second technical scheme.
Figure 18 is the perspective view of dish a in the present invention the second technical scheme.
Figure 19 is the perspective view of burning chamber shell a in the present invention the second technical scheme.
Figure 20 is rotor motion and volume of cylinder change schematic diagram (the power output gear axle of the present invention the first technical scheme
0 ° of moment of corner).
Figure 21 is rotor motion and volume of cylinder change schematic diagram (the power output gear axle of the present invention the first technical scheme
45 ° of moment of corner).
Figure 22 is rotor motion and volume of cylinder change schematic diagram (the power output gear axle of the present invention the first technical scheme
90 ° of moment of corner).
Figure 23 is rotor motion and volume of cylinder change schematic diagram (the power output gear axle of the present invention the first technical scheme
135 ° of moment of corner).
Figure 24 is rotor motion and volume of cylinder change schematic diagram (the power output gear axle of the present invention the first technical scheme
180 ° of moment of corner).
Figure 25 is rotor motion and volume of cylinder change schematic diagram (the power output gear axle of the present invention the first technical scheme
225 ° of moment of corner).
Figure 26 is rotor motion and volume of cylinder change schematic diagram (the power output gear axle of the present invention the first technical scheme
270 ° of moment of corner).
Figure 27 is rotor motion and volume of cylinder change schematic diagram (the power output gear axle of the present invention the first technical scheme
315 ° of moment of corner).
Figure 28 is rotor motion and volume of cylinder change schematic diagram (the power output gear axle of the present invention the first technical scheme
360 ° of moment of corner).
Figure 29 is cylinder maximum and the minimum volume view of the present invention the first technical scheme.
Figure 30 is the instantaneous transmission ratio schematic diagram of an oval gear group engaged transmission.
Figure 31 is two oval gear group resultant gear ratio schematic diagrams that the present invention becomes series relationship.
Figure 32 is that the first rotor of the present invention and the second rotor are relative to power output gear axle fixed skew instantaneous transmission
Compare schematic diagram.
Figure 33 is the present invention normalized combustion chamber volume variable quantity-time curve.
Figure 34 is crankshaft connecting rod type internal combustion engine normalized combustion chamber volume variable quantity-time curve.
Figure 35 is that preferable constant volume cycle (representing by beading fine line I), crankshaft connecting rod type internal combustion engine actual cycle are (with thick empty
Line III represents), the indicator card (p-v figure) of the actual cycle (representing with heavy line II) of the present invention.
In figure: 1, the first rotor, 11, rotating shaft dish, 12, first piston body, the 13, first gyroaxis, 2, cover plate, 21, boss,
22, chimb, the 3, second rotor, the 31, second gyroaxis, the 32, second piston body, 4, dish, 41, upper end plate, 42, lower end plate,
5, burning chamber shell, 51, ceiling, 52, at the bottom of room, 53, porting, 54, pilot hole, 6, gear box casing, the 7, first avette tooth
Wheel, the 8, second oval gear, 9, double oval gear axle, 91, upper oval gear, 92, lower oval gear, 10, power output gear
Axle, 100, spark plug/fuel injector；
1 ', the first rotor a, 12 ', first piston body a, the 13 ', first gyroaxis a, the 2 ', second rotor a, 21 ', second time
Rotating shaft a, the 22 ', second piston body a, 4 ', dish a, 5 ', burning chamber shell a, 53 ', porting a, 6 ', gear box casing a,
10 ', power output gear axle a；
101,102,103,104, roller gear；
201,202,203,204, oval gear；
301, the first gear shaft, the 302, second gear shaft, 303, oval gear axle.
Detailed description of the invention
The present invention is further illustrated with embodiment below in conjunction with the accompanying drawings.
First technical scheme of the present invention: see Fig. 1 to Figure 14, and Figure 20 to Figure 29, double-piston rotor internal-combustion engine, its
It is characterised by: the first rotor 1 is Y-shaped structure, and including rotating shaft dish 11, one end of rotating shaft dish 11 is and the first gyroaxis 13 axis pair
Two the first piston bodies 12 claimed, the other end is provided with the first gyroaxis 13, and the termination of the first gyroaxis 13 is provided with keyway, and first
Gyroaxis 13 axle center is provided with axis hole；
Cover plate 2 is garden plate-like, and the centre of cover plate 2 is provided with the boss 21 of band central through hole, and the periphery of cover plate 2 is provided with convex
Limit 22；The bottom surface of cover plate 2 is connected with first piston body 12 end face；
Second rotor 3 is T-shaped structure, and is provided with the second gyroaxis 31, and one end of the second gyroaxis 31 is provided with and axle
Two the second piston bodies 32 that line is symmetrical, the other end of the second gyroaxis 31 offers keyway, and first piston body 12 and second is lived
The outer circumference diameter of cock body 32 is equal；
Pan Zhou 43 center of dish 4 is provided with axis hole, and the two ends of dish axle 43 connect upper end plate 41 and lower end plate 42, upper end
Dish 41 is in latticed, and upper end plate 41 periphery and lower end plate 42 periphery are provided with screw；Second gyroaxis 31 is threaded onto first time
In the axis hole of rotating shaft 13, the first gyroaxis 13 and the second gyroaxis 31 are all threaded onto in the axis hole at Pan Zhou 43 center, first piston
It is set with burning chamber shell 5 outside body 12 and the second piston body 32；
Burning chamber shell 5 is in peviform, and at the bottom of room, the periphery of 52 is provided with ring flange, and ring flange is provided with screw, combustor
Housing 5 periphery is provided with porting 53, and the offside of burning chamber shell 5 porting 53 is provided with the dress of spark plug/fuel injector 100
Distribution 54, spark plug/fuel injector 100 is fixedly installed in pilot hole 54；The upper end plate 41 of dish 4 and the rotating shaft of the first rotor 1
Dish 11 is adjacent, and the screw of the upper end plate 41 of dish 4 is bolted with the screw of burning chamber shell 5 ring flange；
Gear-box 6 is in peviform, and bottom it, centre is provided with axis hole, and the periphery of gear-box 6 upper end case mouth is provided with ring flange,
Ring flange is provided with screw and lower end plate 42 screw with dish 4 is bolted；The axis hole axis both sides of gear-box 6 are installed
Having double oval gear axle 9, double oval gear axles 9 are equipped with upper oval gear 91 and lower oval gear 92；Second gyroaxis 31 and
Single-revolution axle 13 is threaded onto dish 4 axis hole, and axle head is positioned at gear-box 6, and the axle head of the first gyroaxis 13 is equipped with the first ovum
Shape gear 7, the axle head of the second gyroaxis 31 is equipped with the second oval gear 8, the first oval gear 7 and the second oval gear 8 respectively
Engaging with the upper oval gear 91 of double oval gear axles 9 of both sides in gear-box 6, bottom gear-box 6, to be provided with power defeated for axis hole
Going out gear shaft 10, power output gear axle 10 is provided with two staggered oval gears side by side up and down, and respectively with in gear-box 6
The lower oval gear 92 of double oval gear axles 9 of both sides engages.
Described dish 4 can be monolayer card, is provided with axis hole in the middle of card, and card periphery offers screw.
Burning chamber shell 5, the first rotor 1, cover plate the 2, second rotor 3 are jointly separated out four and are isolated from each other and variable volume
Cylinder, during internal combustion engine operation, corresponding to the uniform rotation of power output gear axle 10, the first rotor 1 and second turn
The rotating speed of son 3 and relative angular position cyclically-varying, these four cylinder the most periodically increase and decrease volumes, and successively
Periodically be in air-breathing, compress, do work, exhaust stroke, thus cylinder of internal-combustion engine produces circulation merit, and by power output gear
Wheel shaft 10 outwards exports power.
Second technical scheme of the present invention: see Figure 15 to Figure 19, double-piston rotor internal-combustion engine, it is characterised in that: burning
Room housing a5 ' is in peviform, and basin mouth periphery is provided with ring flange, is provided with the first rotor a1 ' and second in burning chamber shell a5 '
Rotor a2 '；The first rotor a1 ' is wye piece, and its one end is two first piston bodies of the first gyroaxis a13 ' axisymmetrical
A12 ', the other end is provided with keyway, and the first gyroaxis a13 ' axle center of the first rotor a1 ' is provided with manhole；Second rotor a2 '
For T-piece, its one end is two the second piston body a22 ' of the second gyroaxis a21 ' axisymmetrical, and the other end is provided with keyway；The
Two-revolution axle a21 ' is set in the manhole of the first rotor a1 '；
The center of dish a4 ' offers manhole, and the keyway end of the first rotor a1 ' and the second rotor a2 ' is threaded onto
In the manhole of dish a4 ', the upper and lower card of dish a4 ' the most all offers screw, the upper dish of dish a4 '
Face is adjacent with the first rotor a1 ', and the upper disk surface screw of dish a4 ' is by the flange plate screw hole of bolt with burning chamber shell a5 '
Fixing connection；The lower card screw of dish a4 ' is connected by bolt and gear-box a6 ' flange plate screw hole are fixing；
Gear-box a6 ' is in peviform, and bottom it, centre is provided with axis hole, and the periphery of gear-box a6 ' upper end case mouth is provided with method
Blue dish, ring flange is provided with screw and is connected with the lower card screw of dish a4 ' by bolt；In the middle of gear-box a6 ' bottom
Axis hole is provided with power output gear axle a10 ', and first gear shaft the 301, second gear shaft 302 is symmetrically arranged on power output gear
The axis both sides of wheel shaft a10 ', the upper end of the first gear shaft 301 is provided with the upper end peace of roller gear the 102, second gear shaft 302
Equipped with roller gear 104, the lower end of the first gear shaft 301 is provided with the lower end of oval gear the 201, second gear shaft 302 and installs
There is oval gear 204, two oval gear axles 303 are separately installed with oval gear 202, the upper peace of power output gear axle a10 '
Equipped with oval gear 203, the keyway end of the first gyroaxis a13 ' and the second gyroaxis a21 ' be separately installed with roller gear 101,
103 and respectively correspondence engage with the roller gear 102,104 of the upper end of first, second gear shaft 301,302, first, second tooth
The oval gear 201,204 of the lower end of wheel shaft 301,302 engages respectively with the oval gear 202 on two oval gear axles 303,
Oval gear 202 on two oval gear axles 303 engages with the oval gear 203 on power output gear axle a10 ' simultaneously.
Described dish a4 ' can be monolayer card, is provided with axis hole in the middle of card, and card periphery all offers screw.
Burning chamber shell a5 ', the first rotor a1 ', the second rotor a2 ', dish a4 ' are jointly separated out four and are isolated from each other
And the cylinder of variable volume, during internal combustion engine operation, corresponding to the uniform rotation of power output gear axle a10 ', first turn
Sub-a1 ' and the rotating speed of the second rotor a2 ' and relative angular position cyclically-varying, these four cylinders the most periodically increase and decrease
Variable volume, and be the most periodically in air-breathing, compress, do work, exhaust stroke, thus cylinder of internal-combustion engine produces circulation merit,
And outwards export power by power output gear axle a10 '.
Embodiment 1: first technical scheme of the present invention, double-piston rotor internal-combustion engine, including combustion system, drive system
Deng, see Fig. 1 to Figure 14, and Figure 20 to Figure 29.
The first rotor 1 is Y shape part, and including rotating shaft dish 11, one end of rotating shaft dish 11 is and the first gyroaxis 13 axis pair
Two the first piston bodies 12 claimed, the other end is provided with the first gyroaxis 13, and the termination of the first gyroaxis 13 is provided with keyway, and first
Gyroaxis 13 axle center is provided with axis hole, and cover plate 2 is garden plate-like, cover plate 2 also offers corresponding with position on first piston body 12
Some through holes, use several to pass the bolt of first piston body 12 and cover plate 2 through hole and connect between the first rotor 1 and cover plate 2
Fixing.Second rotor 3 is T-shaped structure, and is provided with the second gyroaxis 31, and one end of the second gyroaxis 31 is provided with and axis pair
Two the second piston bodies 32 claimed, the other end of the second gyroaxis 31 offers keyway, first piston body 12 and the second piston body
The outer circumference diameter of 32 and fan angleThe most equal.Second rotor 3 is co-axially mounted with the first rotor 1 and can relatively rotate, and is entering
Row the second rotor 3 and when being co-axially mounted of the first rotor 1, first by the keyway arrangements end of the second rotor 3 through the first gyroaxis
The axis hole in 13 axle center, the assembling carried out between the first rotor 1 and cover plate 2 the most again is fixed.Pan Zhou 43 center of dish 4 is provided with
Axis hole, the two ends of dish axle 43 connect upper end plate 41 and lower end plate 42, upper end plate 41 in latticed, upper end plate 41 periphery and lower end
Dish 42 periphery is provided with screw；After second gyroaxis 31 is threaded onto in the axis hole of the first gyroaxis 13, then it is threaded onto together
In dish axle 43 central shaft hole.Be set with burning chamber shell 5 outside first piston body 12 and the second piston body 32, burning chamber shell 5 in
Peviform, the ceiling 51 of burning chamber shell 5 is provided with grid hole, and at the bottom of room, the periphery of 52 is provided with ring flange, and ring flange is provided with
Screw, burning chamber shell 5 periphery is provided with porting 53, and the offside of burning chamber shell 5 porting 53 is provided with spark plug/spray
The pilot hole 54 of oil device 100, spark plug/fuel injector 100 is fixedly installed in pilot hole 54.The upper end plate 41 and first of dish 4
The rotating shaft dish 11 of rotor 1 is adjacent, and the screw of the upper end plate 41 of dish 4 passes through bolt with the screw of burning chamber shell 5 ring flange
Connect；Gear-box 6 is in peviform, and bottom it, centre is provided with axis hole, and the power output gear axle 10 of internal combustion engine passes at this hole,
Outwards to export power, the periphery of gear-box 6 upper end case mouth is provided with ring flange, ring flange be provided with screw and with dish 4
Lower end plate 42 screw is bolted.Power output gear axle 10 is provided with two staggered oval gears side by side up and down, and
Engage with the lower oval gear 92 of double oval gear axles 9 of both sides in gear-box 6 respectively.Surrounded by gear-box 6 and dish 4
Space in, the first oval gear 7 is fixed on the keyway arrangements end of the first rotor 1 by bonded mode, and second is avette
Gear 8 is fixed on the keyway arrangements end of the second rotor 3 by bonded mode, and double oval gear axles 9 are equipped with upper avette tooth
Wheel 91 and lower oval gear 92, double oval gear axles have 2, the upper oval gear 91 of one of them double oval gear axle 9 with
First oval gear 7 engaged transmission, lower oval gear 92 and an oval gear engaged transmission of power output gear axle 10, separately
The upper oval gear 91 of one double oval gear axle 9 and the second oval gear 8 engaged transmission, two pairs of oval gear axles 9 times
Oval gear 92 respectively with two oval gear engaged transmission on power output gear axle 10.
First oval gear the 7, second oval gear 8, upper oval gear 91 and lower oval gear 92 and power output gear
Two oval gears on wheel shaft 10, its eccentricity is, its major semiaxis size is equal to each other；The upper ovum of double oval gear axles 9
Shape gear 91 and lower oval gear 92, its major semiaxis direction spatial vertical each other；Two on power output gear axle 10 avette
Gear, its major semiaxis direction spatial vertical the most each other；Sometime, when the first oval gear 7 major semiaxis with nibble mutually
During the upper oval gear 91 semi-minor axis conllinear closed, lower oval gear 92 major semiaxis of this pair of oval gear axle 9 and being meshed therewith
The oval gear semi-minor axis conllinear of power output gear axle 10, now, the semi-minor axis of the second oval gear 8 and being meshed therewith
The upper oval gear 91 major semiaxis conllinear of double oval gear axles 9, now, the first rotor 1 is in transient speed minimum point, second
Rotor 3 is in transient speed peak, and the part plane of symmetry of the first rotor 1 and the second rotor 3 is perpendicular to one another, and each cylinder holds
Long-pending equal.
Due to each moving component of electromotor and the effect of inertia of load, it is believed that the rotating speed n0 on power output gear axle 10
For permanent rotating speed, this permanent rotating speed n0 is respectively by a road " double oval gear axle 9-the first oval gear 7 of power output gear axle 10-"
With another road " double oval gear axle 9-the second oval gear 8 of power output gear axle 10-", every road all includes into series relationship
Two groups of oval gear drive connections, respectively corresponding first oval gear 7 that is the first rotor 1 and the second oval gear 8 that is
The speed change of the second rotor 3 rotates.According to oval gear design specification, eccentricity isOval gear group, its instantaneous transmission ratio
As shown in figure 30, the abscissa in Figure 30 is the rotational angle of drivewheel, and vertical coordinate is the driven pulley instantaneous biography relative to drivewheel
Dynamic ratio, the maximum of its instantaneous transmission ratio is 2, and minima is 0.5, in theory more than instantaneous transmission ratio consecutive variations single order everywhere
Can lead, the most thus can be calculated the technical program and become two groups of oval gear group resultant gear ratios of series relationship as shown in figure 31,
In Figure 31, abscissa is the rotational angle of power output gear axle 10, and vertical coordinate is the first rotor 1 or the second relative power of rotor 3
The instantaneous transmission ratio of output gear shaft 10, the maximum of its instantaneous transmission ratio is 4, and minima is 0.25, instantaneous transmission in theory
Can lead than more than consecutive variations single order everywhere.According to aforesaid first oval gear the 7, second oval gear 8, double oval gear axle
9 and each oval gear relative position relation of power output gear axle 10, it is known that turning on corresponding power output gear axle 10
Speed n0, the instantaneous transmission ratio all cyclically-varyings of transient speed in other words and the difference one of the first rotor 1 and the second rotor 3 are fixed
Phase contrast, as shown in figure 32, if represent the instantaneous transmission ratio of the first rotor 1 in Figure 32 with heavy line, then thick dashed line means that
The instantaneous transmission ratio of the second rotor 3, rotates one week (360 degree) for power output gear axle 10, is represented by two curves respectively
The first rotor 1 and instantaneous transmission ratio two cycles of change of the second rotor 3, and the phase contrast of both is 0.5 instantaneous biography
Dynamic ratio period of change, this shows, during the uniform rotation of power output gear axle 10, the first rotor 1 and the second rotor 3 do
The alternately rotation of acceleration and deceleration, the therefore periodic increase and decrease of angle between the first rotor 1 and the second rotor 3, instantaneous transmission
Ratio can be regarded as the driven gear rotating speed derivative relative to driving gear rotating speed, therefore can pass through in integral and calculating Figure 32 by deficiency and excess two
Some closed area that bar curve surrounds, draws the variable angle amount maximum between the first rotor 1 and the second rotor 3=-=124 degree (about round numbers), the combustor ideal theoretical compression ratio taking the present invention is 11:1, then can calculate every
The fan-shaped angle of individual piston bodyIt is 15.6 degree, in the running of internal combustion engine, first piston body 12 and the second piston body
Between 32, minimum angle is=12.4 degree, maximum angle is=+=136.4 degree, and the most desirable combustion chamber shell
The fan-shaped square hole angle of the porting 53 on body 5It is 15.6 degree, the spacing angle of the fan-shaped square hole of porting 53
It it is 12.4 degree.During internal combustion engine operation, corresponding power output gear axle 10 rotates 1 week, the first rotor 1 and the second rotor 3
Change in location relatively is as shown in Figure 20-Figure 28, in Figure 20-Figure 28, along with the corner of power output gear axle 10 changes, by burning
The volume of four cylinders that room housing 5, the first rotor 1, cover plate the 2, second rotor 3 are separated out jointly periodically increase and decrease, dynamic
Power output gear shaft 10 rotates 1 week, and the first rotor 1 and the second rotor 3 also rotate one week, each volume of cylinder increase and decrease two
Secondary, and be in successively air-breathing, compress, do work, exhaust stroke, then, each cylinder completes that is one thermodynamic cycle of four strokes,
Whole internal combustion engine completes that is four thermodynamic cycles of 16 strokes.
The heat to power output principle of the present invention the first technical scheme is: the gas in each cylinder passes through active force in piston body
Upper and external output work, in any moment, the gas in each cylinder is applied with equal gas to the piston body of cylinder both sides
Pressure effect, therefore this cylinder both sides piston body obtains power equal in magnitude and in opposite direction respectively at this cylinder interior gas
Square effect+(+number this moment direction of expression is identical with piston body angular velocity direction) and-(-number represent this moment direction and
Piston body angular velocity is in opposite direction), the effect axis of moment is the rotary shaft of piston body, and each piston body is made in the moment obtained
With lower respectively with angular velocityWithRotate, the most each piston body obtain respectively at this cylinder interior gas power+
With-, this power, through meshed transmission gear, is the most all delivered to the power output gear axle 10 coalgebra superposition of internal combustion engine
Obtain the clean output work of this cylinder interior gas, it can be seen that, each cylinder interior gas passes through power output gear axle
Gas load square suffered on 10 piston bodies that net work is cylinder side externally exportedWith piston body angle, cylinder both sides speed
The difference of degreeProduct.It can be appreciated that the angular velocity of the fan-shaped volume change of this cylinder interior gas, namely
Saying, owing to the first rotor 1 and the second rotor 3 exist angular velocity difference, therefore cylinder interior gas can be exported by piston body and power
Gear shaft 10 externally exports net work, due to angular velocity difference periodically alternate, the therefore gas of the first rotor 1 and the second rotor 3
Cylinder volume periodically increase and decrease, cylinder the most just can periodically be in air-breathing, compress, does work, in exhaust stroke.
For further illustrating the volume of cylinder Variation Features of the present invention the first technical scheme, the cylinder of this technical scheme is held
Long-pending change procedure normalized, and compared with the volume of cylinder change procedure of the crankshaft connecting rod type internal combustion engine after normalized
Relatively.Normalized method is the method for a kind of nondimensionalization conventional in engineering, the present invention use normalized purpose be in order to
The unified yardstick compared.The normalized method of the present invention is at combustion engine powered output gear shaft 10(or I. C. engine crankshaft) permanent turn
Under the conditions of the reasonable assumption of speed, by the transient change amount that calculates volume of cylinder, (0-1 numerical intervals, cylinder is in minimum
During volume conditions, volume variable quantity is 0, cylinder be in maximum volume state be volume variable quantity be 1) with (0-1 number of corresponding time
Value interval) corresponding relation.Instantaneous with the second rotor 3 relative power output gear axle 10 according to the first rotor 1 shown in Figure 32
Gear ratio relation, draws the present invention the first technical scheme volume of cylinder variable quantity (volume increment) after normalization post processing at any time
Between variation relation as shown in figure 33, corresponding number list is as shown in table 1.
Table 1: normalized combustion chamber volume variable quantity-time relationship numerical tabular
| Time t | Normalization volume variable quantity V |
| 0 | 0.00000 |
| 0.05 | 0.00248 |
| 0.1 | 0.00997 |
| 0.15 | 0.02317 |
| 0.2 | 0.04344 |
| 0.25 | 0.07296 |
| 0.3 | 0.11519 |
| 0.35 | 0.17517 |
| 0.4 | 0.25904 |
| 0.45 | 0.37057 |
| 0.5 | 0.50282 |
| 0.55 | 0.63453 |
| 0.6 | 0.74489 |
| 0.65 | 0.82762 |
| 0.7 | 0.88675 |
| 0.75 | 0.92839 |
| 0.8 | 0.95750 |
| 0.85 | 0.97746 |
| 0.9 | 0.99042 |
| 0.95 | 0.99771 |
| 1 | 1.00000 |
In Figure 33 and Biao 1, rising to the corresponding whole volume of 1(from 0 in time increases the time period), volume of cylinder instantaneous
Increment increases to 1(correspondence volume increment from 0 and arrives maximum from 0).
The normalized exhaust hood volume increment of contrast crankshaft connecting rod type internal combustion engine shown in Figure 34 and Biao 2 becomes in time
Change relation.
Table 2: crankshaft connecting rod type internal combustion engine normalized combustion chamber volume variable quantity-time relationship numerical tabular
| Time t | Normalization volume variable quantity V |
| 0 | 0.00000 |
| 0.05 | 0.00820 |
| 0.1 | 0.03245 |
| 0.15 | 0.07177 |
| 0.2 | 0.12456 |
| 0.25 | 0.18871 |
| 0.3 | 0.26168 |
| 0.35 | 0.34069 |
| 0.4 | 0.42286 |
| 0.45 | 0.50541 |
| 0.5 | 0.58579 |
| 0.55 | 0.66184 |
| 0.6 | 0.73188 |
| 0.65 | 0.79468 |
| 0.7 | 0.84946 |
| 0.75 | 0.89582 |
| 0.8 | 0.93358 |
| 0.85 | 0.96278 |
| 0.9 | 0.98351 |
| 0.95 | 0.99588 |
| 1 | 1.00000 |
Visible, the volume of cylinder pace of change of the present invention the first technical scheme when cylinder instantaneous volumetric is minimum and maximum all
Substantially reduce, thus the thermodynamic cycle of the present invention is more prone to the preferable constant volume cycle that the thermal efficiency is high.
From the multiple thermodynamic cycle indicator cards (p-v figure) shown in Figure 35, preferable constant volume cycle is (by beading fine line I
Representing) area that surrounds on indicator card is maximum, and represent the unit working medium under preferable constant volume cycle, produce circulation merit maximum；Bent
The area that axle connecting rod type internal-combustion engine actual cycle (representing with thick dashed line III) surrounds on indicator card is minimum, represents crankshaft connecting rod type
Unit working medium under internal combustion engine actual cycle, produces circulation merit minimum；The actual cycle (representing with heavy line II) of the present invention exists
Although the area surrounded on indicator card surrounds area less than preferable constant volume cycle, but the actual cycle of the present invention is on indicator card
Surround area ratio crankshaft connecting rod type internal combustion engine actual cycle on indicator card to surround area the most much bigger, thus the present invention
Thermodynamic cycle be more prone to the preferable constant volume cycle that the thermal efficiency is high, the Actual cycle work of the present invention is than crankshaft connecting rod type internal combustion
Machine Actual cycle work substantially increases, thus beneficially the obvious of engine consumption reduces.
Embodiment 2: in the embodiment of the present invention 1, described dish 4 can be cancelled the upper end plate 41 of network-like structure, retain
The screw that the axis hole arranged in the middle of the lower end plate 42 of dish 4, and lower end plate 42 and card periphery are offered so that dish
4 only have monolayer card.That is: dish 4 can be monolayer card, and centre is provided with axis hole, and card periphery all offers screw.Burning
The ring flange of room housing 5, dish 4 pass sequentially through with the ring flange of gear-box 6 that bolt is fixing to be connected.Other and embodiment 1 phase
With.
Embodiment 3: second technical scheme of the present invention, double-piston rotor internal-combustion engine, including combustion system, drive system
Deng, see Figure 15 to Figure 19.
The first rotor a1 ' is Y shape part, and its one end is two the first piston bodies being symmetrical in the first gyroaxis a13 ' axis
A12 ', the other end is provided with keyway, and the first gyroaxis a13 ' axle center of the first rotor a1 ' is provided with manhole.Second rotor a2 '
For T-piece, its one end is two the second piston body a22 ' of the second gyroaxis a21 ' axisymmetrical, and the other end is provided with keyway；The
Two-revolution axle a21 ' is set in the manhole of the first rotor a1 '.The fan of first piston body a12 ' and the second piston body a22 '
Shape angleThe most equal with outer circumference diameter.The center of dish a4 ' offers manhole, the first rotor a1 ' and the second rotor
The keyway end of a2 ' is threaded onto in the manhole of dish a4 ', and the upper and lower card of dish a4 ' the most all offers spiral shell
Hole, the upper disk surface of dish a4 ' is adjacent with the first rotor a1 ', and the upper disk surface screw of dish a4 ' passes through bolt and combustion chamber shell
The flange plate screw hole of body a5 ' is fixing to be connected；The lower card screw of dish a4 ' is by bolt and gear-box a6 ' flange plate screw hole
Fixing connection.Burning chamber shell a5 ' is in peviform, and basin mouth periphery is provided with ring flange, and side opening is provided with porting a53 ', side
Face offers pilot hole relative to porting a53 ' place, and spark plug/fuel injector assembling is fixed at this pilot hole.Combustion chamber shell
Body a5 ', the first rotor a1 ', the second rotor a2 ', dish a4 ' are jointly separated out four and are isolated from each other and four of variable volume
Cylinder, during internal combustion engine operation, along with the first rotor a1 ' and the rotating speed of the second rotor a2 ' and relative angular position change,
These four cylinder the most periodically increase and decrease volumes, and be the most periodically in air-breathing, compress, do work, exhaust stroke.
Gear-box a6 ' is in peviform, and bottom it, centre is provided with axis hole, and power output gear axle a10 ' passes with the most defeated at this axis hole
Going out power, the periphery of gear-box a6 ' upper end case mouth is provided with ring flange, and ring flange is provided with screw and by bolt and dish
The lower card screw of a4 ' connects；.In the space surrounded by gear-box a6 ' and dish a4 ', first, second gear shaft 301,
302 both sides being symmetrically arranged on the axis hole axis in the middle of gear-box a6 ' bottom, the axis hole in the middle of gear-box a6 ' bottom is provided with
Power output gear axle a10 ', the upper end of the first gear shaft 301 is provided with the upper end peace of roller gear the 102, second gear shaft 302
Equipped with roller gear 104, the lower end of the first gear shaft 301 is provided with the lower end of oval gear the 201, second gear shaft 302 and installs
There is oval gear 204, two oval gear axles 303 are provided with oval gear 202, power output gear axle a10 ' is provided with
Oval gear 203, the keyway end of the first gyroaxis a13 ' and the second gyroaxis a21 ' be separately installed with roller gear 101,103 and
Correspondence engages respectively with the roller gear 102,104 of the upper end of first, second gear shaft 301,302, first, second gear shaft
301, the oval gear 201,204 of the lower end of 302 engages respectively with the oval gear 202 on two oval gear axles 303, two
Oval gear 202 on oval gear axle 303 engages with the oval gear 203 on power output gear axle a10 ' simultaneously.
Oval gear 201, oval gear 202, oval gear 203, oval gear 204, its eccentricity is all, it is long by half
Shaft size is equal to each other；Roller gear 101, roller gear 102, roller gear 103, the tooth such as joint garden radius of roller gear 104
Wheel parameter is equal；At a time, the semi-minor axis of oval gear 201 and the major semiaxis of oval gear 202 that is meshed therewith are altogether
Line, now, the semi-minor axis of this oval gear 202 and the major semiaxis conllinear of oval gear 203 being meshed therewith, now, avette
The major semiaxis of gear 204 and the semi-minor axis conllinear of oval gear 202 being meshed therewith, now, the length of this oval gear 202 half
Axle and the semi-minor axis conllinear of oval gear 203 being meshed therewith, now, the first rotor a1 ' is in transient speed peak, and
Two rotor a2 ' are in transient speed minimum point, and the part plane of symmetry of the first rotor a1 ' and the second rotor a2 ' is perpendicular to one another, respectively
Individual volume of cylinder is equal.
Due to each moving component of electromotor and the effect of the inertia of load, it is believed that turning on power output gear axle a10 '
Speed n0 is permanent rotating speed, and this permanent rotating speed n0 is respectively by " power output gear axle a10 '-oval gear axle 303-the first gear shaft
301-roller gear 101 " and " power output gear axle a10 '-oval gear axle 303-the second gear shaft 302-roller gear
Two groups of oval gear drive connections of one-tenth series relationship 103 ", difference Correspondent cy linder gear 101 that is the first rotor a1 ' and circle
The periodicity speed change of stud wheel 103 that is the second rotor a2 ' rotates.According to oval gear design specification, eccentricity isOvum
Shape gear train, as shown in figure 30, the abscissa in Figure 30 is the rotational angle of drivewheel to its instantaneous transmission ratio, and vertical coordinate is driven
Taking turns the instantaneous transmission ratio of relative drivewheel, the maximum of its instantaneous transmission ratio is 2, and minima is 0.5, instantaneous transmission ratio in theory
More than consecutive variations single order everywhere can lead, then can be calculated the technical program and become two groups of oval gear groups of series relationship always to pass
As shown in figure 31, in Figure 31, abscissa is the rotational angle of power output gear axle a10 ' to dynamic ratio, and vertical coordinate is the first rotor a1 '
Or second instantaneous transmission ratio of rotor a2 ' relatively power output gear axle a10 ', the maximum of its instantaneous transmission ratio is 4, minimum
Value is 0.25, more than instantaneous transmission ratio consecutive variations single order everywhere can lead in theory.According to aforesaid oval gear 201, avette
Gear 202, oval gear 203, the relative position relation of oval gear 204, it is known that on corresponding power output gear axle a10 '
The instantaneous transmission ratio all cyclically-varyings of transient speed in other words of rotating speed n0, the first rotor a1 ' and the second rotor a2 ' and difference one
Individual fixing phase contrast, as shown in figure 32, if Figure 32 represents the instantaneous transmission ratio of the first rotor a1 ' with thick dashed line, the most solid
Line means that the instantaneous transmission ratio of the second rotor a2 ', rotates one week (360 degree) corresponding to power output gear axle a10 ', respectively
The first rotor a1 ' represented by two curves and instantaneous transmission ratio 2 cycles of change of the second rotor a2 ', and the phase of both
Potential difference is 0.5 instantaneous transmission ratio period of change, and this shows, during the uniform rotation of power output gear axle a10 ', the
One rotor a1 ' and the second rotor a2 ' does the rotation of alternately acceleration and deceleration, the therefore folder between the first rotor a1 ' and the second rotor a2 '
The periodic increase and decrease in angle, instantaneous transmission ratio can be regarded as the driven gear rotating speed derivative relative to driving gear rotating speed, therefore
The first rotor a1 ' and second can be drawn by some closed area surrounded by two curves of deficiency and excess in integral and calculating Figure 32
Variable angle amount maximum between rotor a2 '=-=124 degree (about round numbers), takes the combustor reason of the present invention
Opinion compression ratio is 11:1, then can calculate the fan-shaped angle of each piston bodyIt is 15.6 degree, in the operation of internal combustion engine
Cheng Zhong, between first piston body a12 ' and the second piston body a22 ', minimum angle is=12.4 degree, maximum angle is=+The fan-shaped square hole angle of the porting 53 ' on=136.4 degree, and the most desirable burning chamber shell 5(angle
Definition with embodiment 1) be 15.6 degree, the spacing angle of the fan-shaped square hole of porting 53(angleDefinition with real
Execute example 1) it is 12.4 degree.During internal combustion engine operation, corresponding power output gear axle 10 rotates 1 week, the first rotor a1 ' and second
The relative change in location of rotor a2 ', refers to situation shown in the embodiment 1 shown in Figure 20 to Figure 28, by burning chamber shell, first
The volume of four cylinders that rotor, the second rotor, dish are separated out jointly periodically increase and decrease, power output gear axle 10
Rotating 1 week, the first rotor and the second rotor also rotate one week, each volume of cylinder increase and decrease secondary, and be in successively air-breathing,
Compression, acting, exhaust stroke, then, each cylinder completes that is one thermodynamic cycle of four strokes, and whole internal combustion engine completes 16
Individual stroke that is four thermodynamic cycle.
The heat to power output principle of third embodiment of the invention, and volume of cylinder Variation Features, identical with first embodiment,
See Figure 33 (table 1) and Figure 35, this is repeated no more.
Embodiment 4: in the embodiment of the present invention 3, dish a4 ' can be monolayer card, and centre is provided with axis hole, card periphery
All offer screw.It is solid that the ring flange of burning chamber shell a5 ', dish a4 ' and the ring flange of gear-box a6 ' pass sequentially through bolt
Fixed connection.Other is same as in Example 3.
The present invention has a following advantageous application effect:
1, can significantly reduce engine consumption, improve fuel economy, improve engine exhaust emission.Master of the present invention
If by following technological approaches realize this application effect:
First, with the crankshaft connecting rod type combustion chambers of internal combustion engines volume change-time relationship characteristic phase shown in Figure 34 and table 2
Combustion chamber volume change-time relationship characteristic of the present invention shown in ratio, Figure 33 and table 1, shows that the volume of cylinder of the present invention is at it
Change the slowest time minimum or maximum.When cylinder interior gas is in the compression stroke later stage, volume of cylinder pace of change will slowly
In being conducive to provide cylinder, combustible oil gas mixture fully burns the required time, it is thus possible to allow the electronic spark advance of electromotor
Angle greatly reduces, and substantially reduces the compression negative work of cylinder interior gas, adds the circulation merit of electromotor；And when being in cylinder
When power stroke initiates, also due to volume of cylinder is to start to be slowly increased from its minima so that in cylinder, combustible oil gas mixes
More abundant with thing burning, fuel oil supply just can produce higher inner pressure of air cylinder peak as crankshaft connecting rod type internal combustion engine
Value, thus add the circulation merit of electromotor, and improve the waste gas discharge of electromotor.Thus engine consumption can be reduced, carry
High fuel economy, improves engine exhaust emission.
From the multiple thermodynamic cycle indicator cards (p-v figure) shown in Figure 35, preferable constant volume cycle is (by beading fine line I
Representing) area that surrounds on indicator card is maximum, represents that the unit working medium under preferable constant volume cycle produces circulation merit maximum, bent axle
The area that connecting rod type internal-combustion engine actual cycle (representing with thick dashed line III) surrounds on indicator card is minimum, in representing crankshaft connecting rod type
It is minimum that unit working medium under combustion engine actual cycle produces circulation merit, and the actual cycle (representing with heavy line II) of the present invention is showing merit
Although the area surrounded on figure is less than the area that surrounds of preferable constant volume cycle, but the actual cycle of the present invention enclosing on indicator card
Become area ratio crankshaft connecting rod type internal combustion engine actual cycle on indicator card to surround area the most much bigger, thus the heat of the present invention
Power circulation is more prone to the preferable constant volume cycle that the thermal efficiency is high, and the Actual cycle work of the present invention is more real than crankshaft connecting rod type internal combustion engine
Border circulation merit substantially increases, thus beneficially the obvious of engine consumption reduces, and improves fuel economy, improves engine exhaust
Discharge.
Secondly, according to relevant information, in crankshaft connecting rod type internal combustion engine inner carrier reciprocatory movement, between piston and cylinder wall
Friction loss, consume the 10%-20% of cycle of engine merit.In the piston body rotation process of the present invention, piston body and combustion
The friction loss burning body housing is the least, is substantially negligible and disregards.Thus add the clean output work of electromotor, hence it is evident that reduce
Engine consumption, improves fuel economy.
Again, compared with triangle rotor type electromotor.When the present invention constitutes relative motion between each parts of cylinder
It is face contact.Therefore the sealing of cylinder easily realizes, good sealing effect, and cylinder leakage tester loss when electromotor runs is little, energy
Reduce engine consumption, improve fuel economy, improve engine exhaust emission.
2, the power to weight ratio of electromotor can be greatly improved.The present invention mainly realizes this by following technological approaches should
By effect:
First, relative to crankshaft connecting rod type internal combustion engine, the present invention is without complicated throttle valve structure；Drive mechanism is also by body
The crankshaft rod structure that long-pending weight is big has changed over the gear structure of compact conformation；Air cylinder structure also obvious densification.Same
Under sample gas cylinder displacement, the present invention can have the least many volume and weights, therefore can improve the power to weight ratio of electromotor.
Secondly, with the crankshaft connecting rod type combustion chambers of internal combustion engines volume change-time relationship characteristic phase shown in Figure 34 and table 2
Combustion chamber volume change-time relationship characteristic of the present invention shown in ratio, Figure 33 and table 1, shows that the volume of cylinder of the present invention is at it
Change the slowest time minimum or maximum.It is to say, when cylinder is in exhaust stroke end of a period, now air vent diminishes, the present invention
Volume of cylinder minimizing speed is beneficial to aerofluxus fully slowly, and reduces exhaust process windage loss；When cylinder is in air-breathing
During end of stroke, now air inlet diminishes, and present invention volume of cylinder slowly gathers way and is also beneficial to suck newly
Fresh oil gas mixture, and reduce breathing process windage loss.This is beneficial to improve engine breathing efficiency, also to engine thermal
The raising of cycle efficieny gain, improves the power per liter of electromotor, it is thus possible to improve the power to weight ratio of electromotor.
Again, improving and the increase of clean output work of the efficiency of cycle of the present invention that Figure 35 shows, it helps electromotor
The raising of power to weight ratio.
Finally, compared with existing crankshaft connecting rod type internal combustion engine, all driving members of the present invention are all axialy symmetric part, thus
Electromotor is allowed to have higher limit speed；From the point of view of the efficiency of combustion of electromotor, the combustor of the present invention shown in Figure 33 (table 1)
Volume change-time relationship characteristic also will assist in electromotor and is maintained to higher efficiency of combustion at high speed.Cause
This, the present invention has the good potentiality of high-power output under high rotating speed.When the present invention is as aircraft power plant or other needs
During the application of higher power to weight ratio, the power to weight ratio of electromotor can be greatly improved by improving the rotating speed of electromotor.
3, engine structure is simple, and anufacturability is good.The present invention mainly realizes this by following technological approaches should
By effect:
First, the building block of the present invention is few, does not has the complicated throttle valve structure of crankshaft connecting rod type electromotor and bent axle to connect
Bar structure etc..
Secondly, manufacturing and designing of each building block of the present invention all has ripe technological procedure, without special fabrication processes
The parts required, as oval gear transmission is widely used in terms of textile machine and agricultural machinery etc., and cylinder seal can be used for reference
Piston ring packing mode of crankshaft connecting rod type internal combustion engine etc..
4, engine luggine and noise level are low, smooth running, and moving component is few, and the electromotor working service life-span is long.This
Invention mainly realizes this application effect by following technological approaches:
First, compared with existing crankshaft connecting rod type internal combustion engine, each moving component of the present invention is all axialy symmetric part, can have
Imitating the various vibrations and noise avoiding moving component to cause due to mass unbalance, electromotor smoothness of operation is good, working service
Life-span is long.
Secondly, as shown in figure 30, each movement transmission members of the present invention, its instantaneous transmission ratio consecutive variations is everywhere in theory
More than single order can lead, therefore without rigid shock between drive disk assembly, also without soft impulse；And the transmission of each movement transmission members
Journey can be mated well with the pressure change procedure of cylinder interior gas, it is thus possible to be prevented effectively from moving component due to transmission impact cause
Various vibrations and noise, electromotor smoothness of operation is good, and the working service life-span is long.
Finally, the building block of the present invention is few, and moving component is few, and friction loss is little, does not has crankshaft connecting rod type electromotor
Complicated throttle valve structure and crankshaft rod structure etc., therefore breakdown in the motor rate is low, and the working service life-span is long.
5, engine structure is compact.The present invention mainly realizes this application effect by following technological approaches:
Relative to crankshaft connecting rod type internal combustion engine, the present invention does not has the throttle valve structure of complexity, and drive mechanism is also big by volume
The crankshaft rod structure that weight is big has changed over the gear structure of compact conformation, air cylinder structure also obvious densification.Therefore, exist
Under same displacement volume, the present invention can have the least many volume and weights, and compact conformation on the whole can be the most applicable
In electromotor overall size being required the application scenarios such as strict aircraft power plant.
6, engine power output moment of torsion is big.The present invention mainly realizes this application effect by following technological approaches:
The power output gear axle of the present invention rotates one week, four cylinders respectively complete once to include air-breathing, compress, do work,
The thermodynamic cycle of four strokes of aerofluxus, and with four cylinder crankshaft connecting rod type internal combustion engines of discharge capacity, then rotate two circles for bent axle, four
Individual cylinder respectively complete once to include air-breathing, compress, do work, the thermodynamic cycle of four strokes of aerofluxus.The acting speed of the present invention is
With discharge capacity with two times of crankshaft connecting rod type internal combustion engine of rotating speed；Consider further that the thermal efficiency height of the present invention, cylinder power per liter height, machine
The favorable factors such as tool friction loss little output net power is big.Therefore the power output moment of torsion of the present invention is the same discharge capacity song with rotating speed
More than two times of axle connecting rod type internal-combustion engine.
7, electromotor multiple design parameter adjustable.The present invention mainly realizes this application effect by following technological approaches
Really:
Such as, the fan-shaped angle of inventive piston body is increased and decreased, the ideal theoretical compression ratio of changeable electromotor；Change the present invention
The eccentricity of each oval gear, can change the maximum cylinder volume of electromotor；By changing two ovum of power output gear axle
Between the major axis of shape gear, angle changes the first rotor of the present invention and bitrochanteric angular velocity cycle fixed skew, can change
Become the volume of cylinder-time behavior of electromotor, etc..
8, only needing the least structure design to adjust, the present invention can change into high performance pump.The present invention mainly passes through
Following technological approaches realize this application effect:
For embodiments of the invention 1 and embodiment 3, it is only necessary to the spark plug/fuel injector 100 on internal combustion engine housing is pacified
Dress arranges, at hole, the another set of porting being symmetrical in existing porting, can change the present invention into pump；For the present invention's
Embodiment 3, it is also possible to by the joint garden radius of roller gear 101 and roller gear 103, all change the most meshed cylinder into
Gear 102 and roller gear 104 save 0.5 times of garden radius, can change the present invention into pump.
The pump developed by embodiments of the invention 1 and embodiment 3, compact conformation；Flow is big；Boosting capability is strong；With
Time, due to the cylinder body volume change-time relationship characteristic of the present invention shown in Figure 33 and table 1 so that this pump can be opened at fluid inlet
Close initial stage circulation area little in the case of allow relatively low fluid inlet pressure, this pump can also effectively relax fluid issuing opening and closing
Cylinder interior pressure impact phenomenon under the conditions of initial stage small circulation area.Thus, the present invention pump changed, multiple performance refers to
Mark the highest.
Claims (4)
1. double-piston rotor internal-combustion engine, it is characterised in that: the first rotor is Y shape structure, including rotating shaft dish, one end of rotating shaft dish
For two first piston bodies with the first gyroaxis axisymmetrical, the other end is provided with the first gyroaxis, the end of the first gyroaxis
Head is provided with keyway, and the first gyroaxis axle center is provided with axis hole；Cover plate is discoid, and the centre of cover plate is provided with the convex of band central through hole
Platform, the periphery of cover plate is provided with chimb；The bottom surface of cover plate is connected with first piston end face；Second rotor is T-shaped structure, and sets
Being equipped with the second gyroaxis, one end of the second gyroaxis is provided with two the second piston bodies with axisymmetrical, the second gyroaxis
The other end offers keyway, and the outer circumference diameter of first piston body and the second piston body is equal；The Pan Zhou center of dish is provided with axle
Hole, the two ends of dish axle connect upper end plate and lower end plate, and upper end plate is latticed, and upper end plate periphery and lower end plate periphery are all provided with
It is equipped with screw；Second gyroaxis is threaded onto in the axis hole of the first gyroaxis, and the first gyroaxis and the second gyroaxis are all threaded onto dish
In the axis hole at axle center, outside first piston body and the second piston body, it is set with burning chamber shell；Burning chamber shell is in peviform, room
The periphery at the end is provided with ring flange, and ring flange is provided with screw, and burning chamber shell periphery is provided with porting, and burning chamber shell enters
The offside of air vent is provided with the pilot hole of spark plug/fuel injector, and spark plug/fuel injector is fixedly installed in pilot hole；Dish
Upper end plate adjacent with the rotating shaft dish of the first rotor, the screw of the upper end plate of dish and the screw of burning chamber shell ring flange lead to
Cross bolt to connect；Gear-box is peviform, and bottom it, centre is provided with axis hole, and the periphery of gear-box upper end case mouth is provided with flange
Dish, ring flange is provided with screw and the valve snail hole, lower end with dish is bolted；The axis hole axis both sides of gear-box are installed
Having double oval gear axle, double oval gear axles are equipped with upper oval gear and lower oval gear；Second gyroaxis and the first gyroaxis
Being threaded onto dish axis hole, and axle head is positioned at gear-box, the first gyroaxis axle head is equipped with the first oval gear, the second gyroaxis
Axle head equipped with the second oval gear, the first oval gear and the second oval gear respectively with double oval gears of both sides in gear-box
The upper end oval gear engagement of axle, bottom gear-box, axis hole is provided with power output gear axle, and power output gear axle is provided with
Two staggered oval gears side by side up and down, and nibble with the lower oval gear of double oval gear axles of both sides in gear-box respectively
Close.
2. double-piston rotor internal-combustion engine, it is characterised in that: burning chamber shell a is in peviform, and basin mouth periphery is provided with ring flange, combustion
In burning room housing a, the first rotor a and the second rotor a is installed；The first rotor a is wye piece, and its one end is the first gyroaxis a
Two first piston body a of axisymmetrical, the other end is provided with keyway, and the first gyroaxis a axle center of the first rotor a is provided with circle
Through hole；Second rotor a is T-piece, and its one end is two the second piston body a of the second gyroaxis a axisymmetrical, and the other end sets
There is keyway；Second gyroaxis a is set in the manhole of the first rotor a；Dish a includes upper disk surface and lower card, described
The center of upper disk surface and lower card is provided with through hole and is connected by axle sleeve, and the upper and lower card of dish a is the most all offered
Screw, the keyway end of the first rotor a and the second rotor a is had to be threaded onto in the axle sleeve of dish a, the upper disk surface of dish a
Adjacent with the first rotor a, the upper disk surface screw of dish a is connected by bolt and burning chamber shell a flange plate screw hole are fixing；
The lower card screw of dish a is connected by bolt and gear-box a flange plate screw hole are fixing；Gear-box a is peviform, bottom it in
Between be provided with axis hole, the periphery of gear-box a upper end case mouth is provided with ring flange, and ring flange is provided with screw and by bolt and dish type
The lower card screw of part a connects；Axis hole in the middle of bottom gear-box a is provided with power output gear axle a, first, second gear
Axial symmetry is installed on the axis both sides of power output gear axle a, and the upper end of the first gear shaft is provided with roller gear, the second gear
The upper end of axle is provided with roller gear, and the lower end of the first gear shaft is provided with oval gear, the lower end of the second gear shaft is provided with
Oval gear, two oval gear axles is separately installed with oval gear, power output gear axle a is provided with oval gear,
The keyway end of the first gyroaxis a and the second gyroaxis a is separately installed with roller gear and corresponding upper with first, second gear shaft
End roller gear engage respectively, the oval gear of the lower end of first, second gear shaft respectively with on two oval gear axles
Oval gear engages, and the oval gear on two oval gear axles engages with the oval gear on power output gear axle a simultaneously.
Double-piston rotor internal-combustion engine the most according to claim 1, it is characterised in that: described dish is monolayer card, dish
Being provided with axis hole in the middle of face, card periphery offers screw.
Double-piston rotor internal-combustion engine the most according to claim 2, it is characterised in that: described dish a is monolayer card, dish
Being provided with axis hole in the middle of face, card periphery offers screw.
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| CN104727936B (en) * | 2015-01-22 | 2017-03-08 | 唐仁杰 | Double-piston rotary internal combustion engine |
| KR20160129780A (en) * | 2015-04-30 | 2016-11-09 | 최영희 | Internal combustion engine using the dual turbine |
| CN104989520A (en) * | 2015-06-11 | 2015-10-21 | 南京航空航天大学 | Parallel staggered rotating swing type engine |
| CN106968922B (en) * | 2017-04-11 | 2019-02-19 | 上乘精密科技（苏州）有限公司 | A kind of air compression plant shell |
| CN109185135B (en) * | 2018-09-14 | 2022-03-11 | 武汉豪岩照明电子有限公司 | Concentric blade piston air pump |
| CN113006932B (en) * | 2021-04-15 | 2022-05-03 | 北京理工大学 | Direct-injection rotary opposed-piston engine |
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| CN2313052Y (en) * | 1997-05-08 | 1999-04-07 | 吴素良 | Dual-rotating non-linear drive piston-type internal combustion engine |
| CN101196124A (en) * | 2007-08-08 | 2008-06-11 | 邵文英 | Vane type cavity capability changing device, vane type gas engine and vane compressor |
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| CN204344266U (en) * | 2014-12-24 | 2015-05-20 | 唐仁杰 | Double-piston rotor internal-combustion engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US6994071B2 (en) * | 2002-05-17 | 2006-02-07 | Schwam Paul A | Two-cycle engine for counter-rotation especially for aviation applications |
| US7703433B2 (en) * | 2007-02-28 | 2010-04-27 | Richard Colman Webster | Rotary internal combustion engine and rotary compressor |
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| CN2313052Y (en) * | 1997-05-08 | 1999-04-07 | 吴素良 | Dual-rotating non-linear drive piston-type internal combustion engine |
| CN101196124A (en) * | 2007-08-08 | 2008-06-11 | 邵文英 | Vane type cavity capability changing device, vane type gas engine and vane compressor |
| CN101592072A (en) * | 2008-05-26 | 2009-12-02 | 张振明 | Double-rotor controlled alternate-running engine |
| CN204344266U (en) * | 2014-12-24 | 2015-05-20 | 唐仁杰 | Double-piston rotor internal-combustion engine |
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Effective date of registration: 20190924 Address after: Ganquan road Shushan District of Hefei City, Anhui Province, 230000 West hillock road to the South Wild Garden commercial office building room B-2705 Patentee after: Hefei wisdom Dragon Machinery Design Co., Ltd. Address before: 330024 Jiangxi province Qingyunpu District of Nanchang City Road Bridge Hongdu a District 38 building 902 room Patentee before: Tang Ren Jie |
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